CN109765016B - Method and device for testing axial dynamic stiffness of main shaft - Google Patents
Method and device for testing axial dynamic stiffness of main shaft Download PDFInfo
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Abstract
The invention discloses a method for testing axial dynamic stiffness of a main shaft, which comprises the following steps: a bearing plate is arranged on the main shaft; respectively arranging hydrostatic bearings at the two opposite sides of the bearing plate in a clearance manner along the axial direction of the main shaft; driving the main shaft to rotate; two constant delivery pumps are adopted to respectively correspondingly input oil into the oil cavities of the two hydrostatic bearings, and the oil is sprayed to the bearing plate through the oil cavities of the hydrostatic bearings; testing the axial displacement of the bearing plate by using a displacement sensor, and determining the axial displacement x of the main shaft according to the axial displacement of the bearing plate; calculating the effective bearing area S of an oil cavity of the hydrostatic bearing; calculating the oil discharge hydraulic resistance R of the oil cavity of the hydrostatic bearing0(ii) a And calculating the axial dynamic stiffness k of the main shaft. The invention can reduce vibration and avoid safety accidents caused by collision and abrasion. The invention also discloses a device for testing the axial dynamic stiffness of the main shaft.
Description
Technical Field
The invention relates to the technical field of main shafts, in particular to a method and a device for testing axial dynamic stiffness of a main shaft.
Background
At present, a main shaft of a high-speed machine tool is a core functional component of a modern machine tool, and the main shaft of the high-speed machine tool is used for driving a cutter (a grinding wheel) or a workpiece to rotate so as to realize high-speed precision machining. Along with the continuous improvement of the requirements of modern industry on the machining precision and the machining efficiency of the machine tool, the requirements of the machine tool on the performance of the main shaft are higher and higher. The rigidity is one of the important indexes for measuring the performance of the main shaft of the high-speed machine tool. The rigidity of the main shaft comprises static rigidity in a static state and dynamic rigidity in high-speed operation. The rigidity testing method which is feasible in engineering and widely adopted at present is a static rigidity testing method. However, the static stiffness cannot truly reflect the deformation resistance of the spindle under the condition of bearing cutting load during high-speed operation, and only the dynamic stiffness can scientifically reflect the dynamic bearing characteristic of the spindle.
The prior dynamic stiffness testing method in engineering comprises the following steps: the rolling bearing type loading measurement method is characterized in that a rolling bearing is directly used as a loading bearing, and the excircle of the loading bearing is contacted with the excircle of a main shaft overhanging end, so that the main shaft is loaded; however, this approach has the following drawbacks:
(1) the loading bearing rotates at a high speed along with the main shaft, so that the noise is high and the vibration is large;
(2) the loading bearing is in smooth normal contact with the excircle of the main shaft, so that the loading bearing is easy to damage due to heat generated by collision and grinding.
Disclosure of Invention
In order to overcome the defects of the prior art, the invention aims to provide a method for testing the axial dynamic stiffness of the main shaft, and the invention aims to provide a device for testing the axial dynamic stiffness of the main shaft, which adopts a hydrostatic bearing arranged in a gap to realize loading, and the hydrostatic bearing and a bearing plate have a gap, so that the vibration can be reduced, and safety accidents caused by collision and abrasion can be avoided.
One of the purposes of the invention is realized by adopting the following technical scheme:
a method for testing axial dynamic stiffness of a main shaft comprises the following steps:
the preparation method comprises the following steps: a bearing plate is arranged on the main shaft; respectively arranging hydrostatic bearings at two opposite sides of the bearing plate along the axial direction of the main shaft in a clearance mode, enabling the initial clearances between the two hydrostatic bearings and the bearing plate to be the same, and enabling oil cavities of the two hydrostatic bearings to be oppositely arranged;
and a load applying step: driving the main shaft to rotate; two constant delivery pumps are adopted to respectively correspondingly input oil into the oil cavities of the two hydrostatic bearings, and the oil is sprayed to the bearing plate through the oil cavities of the hydrostatic bearings; at the same time, the rotating speed V of one of the constant delivery pumps is adjusted1Is adjusted to n0+nxAnd the rotational speed V of the other fixed displacement pump is adjusted2Is adjusted to n0-nx；
An axial displacement acquisition step: in the step of applying the load, a displacement sensor is adopted to test the axial displacement of the bearing plate, and the axial displacement x of the main shaft is determined according to the axial displacement of the bearing plate;
a calculation step:
calculating the effective bearing area S of the oil cavity of the hydrostatic bearing according to an area calculation formula;
calculating the oil outlet hydraulic resistance R of the oil cavity of the hydrostatic bearing0；
Calculating the axial dynamic stiffness k of the main shaft according to the formula (1);
wherein, in the above formula (1):
x is the axial displacement of the spindle; s is the effective bearing area; n is0The rated rotating speed of the fixed displacement pump; n isxIs the rotational speed V1Or speed of rotation V2A variation amount with respect to the rated rotation speed; q. q.s0The rated oil quantity pumped out by the fixed displacement pump every time the fixed displacement pump rotates one circle; r0The oil outlet liquid resistance is set; h is0Is the initial gap size between the hydrostatic bearing and the carrier plate.
Further, in the axial displacement obtaining step, the two displacement sensors are used for testing the axial displacement of the bearing plate, and the average value of the values tested by the two displacement sensors is taken as the axial displacement x of the main shaft.
Further, in the step of applying the load, the current supplied to the fixed displacement pump is controlled by a frequency converter so as to adjust the rotating speed of the fixed displacement pump.
Further, a flange is used as the bearing plate.
The second purpose of the invention is realized by adopting the following technical scheme:
an axial dynamic stiffness testing device of a main shaft comprises a bearing plate, a bearing seat, an oil storage container, a displacement sensor, two hydrostatic bearings, two constant delivery pumps and two frequency converters; the bearing seat is provided with an inner cavity; the bearing plate is movably arranged in the inner cavity; the two hydrostatic bearings are respectively arranged on two opposite sides of the bearing plate along the axial direction of the bearing plate and are respectively arranged on the bearing seats; the oil cavities of the two hydrostatic bearings are oppositely arranged, and a gap is formed between the hydrostatic bearings and the bearing plate; the two constant delivery pumps are arranged in one-to-one correspondence with the two hydrostatic bearings and are used for conveying the oil in the oil storage container to the oil cavities corresponding to the hydrostatic bearings; the two frequency converters are arranged in one-to-one correspondence with the two fixed displacement pumps; the output end of the frequency converter is electrically connected with the input end of the corresponding constant delivery pump, and the input end of the frequency converter is communicated with an external power supply; the displacement sensor is installed on the bearing seat and used for testing the axial displacement of the bearing plate.
Furthermore, the number of the displacement sensors is two, and the two displacement sensors are sequentially arranged along the axial direction of the bearing plate.
Furthermore, the hydrostatic bearing is also provided with an oil return groove and an oil return channel; the notch of the oil return groove faces the bearing plate; the oil return groove is communicated with the oil return groove and the inner cavity; the oil return passage is connected with an oil return pipe, and one end of the oil return pipe, which is far away from the oil return passage, extends into the oil storage container.
Furthermore, the bearing seat is provided with an oil return port communicating the outside with the inner cavity.
Compared with the prior art, the invention has the beneficial effects that:
the invention adopts the technical scheme that a bearing plate is fixed on a shaft core, hydrostatic bearings are respectively arranged at the two sides of the bearing plate in a clearance manner, and the rotating speed is respectively adjusted to be n0+nxAnd n0-nxThe two constant delivery pumps respectively input oil for the two hydrostatic bearings, and the oil is sprayed to the bearing plate through oil cavities of the hydrostatic bearings to load the bearing plate and drive the main shaft to rotate by the bearing plate; the axial displacement of the main shaft can be obtained by matching with a displacement sensor, so that the dynamic stiffness of the main shaft can be tested; in the whole process, a gap exists between the hydrostatic bearing and the bearing plate, so that safety accidents caused by collision and abrasion can be avoided; moreover, the bearing plate is not in contact with the working state of the hydrostatic bearing, and an oil film formed in the hydrostatic bearing has vibration absorption characteristics, so that vibration is reduced, and the bearing plate has excellent vibration absorption performance.
Drawings
FIG. 1 is a flow chart of a method for testing axial dynamic stiffness of a spindle according to the present invention;
FIG. 2 is a schematic structural diagram of an axial dynamic stiffness testing device of a spindle according to the present invention;
fig. 3 is a schematic structural diagram of the axial dynamic stiffness testing device of the main shaft (excluding the oil storage container and the frequency converter).
In the figure: 10. a main shaft; 20. a carrier plate; 30. a bearing seat; 31. an inner cavity; 40. an oil storage container; 50. a displacement sensor; 60. a hydrostatic bearing; 61. an oil cavity of the hydrostatic bearing; 70. a constant delivery pump; 80. a frequency converter; 90. an oil return groove; 100. an oil return passage; 110. and an oil return port.
Detailed Description
The present invention will be further described with reference to the accompanying drawings and the detailed description, and it should be noted that any combination of the embodiments or technical features described below can be used to form a new embodiment without conflict.
The method for testing the axial dynamic stiffness of the main shaft shown in FIG. 1 comprises the following steps:
the preparation method comprises the following steps: mounting a carrier plate 20 on the main shaft 10; hydrostatic bearings 60 are respectively arranged on two opposite sides of the bearing plate 20 along the axial direction of the main shaft 10 in a clearance manner; the initial gap between each of the two hydrostatic bearings 60 and the carrier plate 20 is the same, i.e. the gap between one hydrostatic bearing 60 and the carrier plate 20 is the same as the gap between the other hydrostatic bearing 60 and the carrier plate 20; the cavities of the two hydrostatic bearings 60 are oppositely arranged, so that the loading positions of the two hydrostatic bearings 60 on the bearing plate 20 are the same;
and a load applying step: driving the main shaft 10 to rotate; two constant delivery pumps 70 are adopted to respectively correspondingly input oil into the oil cavities 61 of the two hydrostatic bearings, and at the moment, the constant delivery pumps 70 input external oil into the oil cavities 61 of the hydrostatic bearings; then the bearing plate 20 is sprayed from an oil cavity 61 of the hydrostatic bearing to the bearing plate 20, so that the bearing plate 20 is loaded, and the bearing plate 20 is arranged on the main shaft 10, so that the main shaft 10 is loaded; at the same time, the rotation speed V of one of the constant flow pumps 70 is adjusted1Is adjusted to n0+nxAnd the rotational speed V of the other fixed displacement pump 70 is adjusted2Is adjusted to n0-nxBecause the rotating speeds of the two constant delivery pumps 70 are different, namely the oil supply pressures of the two constant delivery pumps 70 are different, the loading force of oil sprayed to the bearing plate 20 is different, and the bearing plate 20 can drive the shaft core to move along the axial direction of the shaft core;
an axial displacement acquisition step: in the step of applying the load, the axial displacement of the bearing plate 20 is tested by using the displacement sensor 50, and as the bearing plate 20 is fixedly connected with the shaft core, the axial displacement x of the spindle 10 is determined according to the axial displacement of the bearing plate 20;
a calculation step:
calculating the effective bearing area S of the oil cavity 61 of the hydrostatic bearing according to an area calculation formula;
calculating the oil discharge hydraulic resistance R of the oil chamber 61 of the hydrostatic bearing0；
Calculating the axial dynamic stiffness k of the main shaft 10 according to the formula (1);
wherein, in the above formula (1):
x is the axial displacement of the spindle 10; s is the effective bearing area of the oil chamber 61 of the hydrostatic bearing; n is0Is the rated rotational speed of the fixed displacement pump 70; n isxIs the rotational speed V1Or speed of rotation V2A variation amount (absolute value) with respect to the rated rotation speed; q. q.s0The rated oil amount pumped out for each rotation of the constant delivery pump 70; r0The oil outlet hydraulic resistance of the oil chamber 61 of the hydrostatic bearing; h is0Is the initial gap size between the hydrostatic bearing 60 and the carrier plate 20;
in the above steps, the hydrostatic bearing 60 and the fixed displacement pump 70 are matched to load the main shaft 10, and a gap exists between the hydrostatic bearing 60 and the bearing plate 20, so that safety accidents caused by collision and abrasion can be avoided; furthermore, the bearing plate 20 is not in contact with the hydrostatic bearing 60 in the operating state, and the oil film formed in the hydrostatic bearing 60 has a vibration absorption characteristic, so that vibration is reduced, and the bearing plate has excellent vibration absorption performance.
It should be noted that the effective bearing area S and the oil discharge resistance R are described above0The calculation formula (b) is common knowledge, and can be known by those skilled in the art according to common knowledge, and will not be described herein again.
Preferably, in the axial displacement obtaining step, two displacement sensors 50 are used to test the axial displacement of the bearing plate 20, and the average value of the values tested by the two displacement sensors 50 is taken as the axial displacement x of the spindle 10; the accuracy can be improved by obtaining the axial displacement of the spindle 10 from the average of the two sensors.
Further, in the step of applying the load, the magnitude of the current supplied to the fixed displacement pump 70 is controlled using the frequency converter 80 to adjust the rotation speed of the fixed displacement pump 70.
Specifically, a flange is employed as the carrier plate 20.
The embodiment also discloses a device for testing axial dynamic stiffness of a main shaft as shown in fig. 2-3, which comprises a bearing plate 20, a bearing seat 30, an oil storage container 40, a displacement sensor 50, two hydrostatic bearings 60, two fixed displacement pumps 70 and two frequency converters 80; the bearing seat 30 is formed with an inner cavity 31; the bearing plate 20 is movably arranged in the inner cavity 31; the two hydrostatic bearings 60 are respectively arranged on two opposite sides of the bearing plate 20 along the axial direction of the bearing plate 20 and are respectively arranged on the bearing seats 30; the oil cavities 61 of the two hydrostatic bearings are oppositely arranged, and a gap is formed between the hydrostatic bearing 60 and the bearing plate 20; the two fixed displacement pumps 70 are arranged in one-to-one correspondence with the two hydrostatic bearings 60, and the fixed displacement pumps 70 are used for conveying the oil in the oil storage container 40 into the oil chambers 61 of the corresponding hydrostatic bearings; the two frequency converters 80 are arranged corresponding to the two constant delivery pumps 70 one by one; the output end of the frequency converter 80 is electrically connected with the input end of the corresponding constant delivery pump 70, and the input end of the frequency converter 80 is communicated with an external power supply; the displacement sensor 50 is mounted on the bearing housing 30 and is used to test the axial displacement of the carrier plate 20.
On the basis of the structure, when the axial dynamic stiffness testing device of the main shaft is used, the main shaft 10 penetrates into the inner cavity 31 and is fixedly connected with the bearing plate 20; moving the carrier plate 20 to make the gap between the carrier plate 20 and the two hydrostatic bearings 60 consistent; rotating the main shaft 10, controlling the voltage of the power supply of the constant delivery pumps 70 by using the frequency converter 80, and adjusting the rotation speed of one of the constant delivery pumps 70 to n0+nxAnd the rotational speed V of the other fixed displacement pump 70 is adjusted2Is adjusted to n0-nxAt this time, the oil supply pressure of the two fixed displacement pumps 70 is not used, and simultaneously the fixed displacement pumps 70 convey the oil in the oil storage container 40 into the oil cavity 61 of the hydrostatic bearing, and the oil is stored in the oil cavity 61 of the hydrostatic bearing and then is sprayed to the bearing plate 20, so that the bearing plate 20 is loaded, and the bearing plate 20 is fixedly connected with the main shaft 10, so that the main shaft 10 is loaded; furthermore, the loading force on the two opposite sides of the bearing plate 20 is different, so that the bearing plate moves in the axial direction and drives the spindle 10 to move in the axial direction; at this time, the displacement sensor 50 tests the axial displacement of the bearing plate 20, i.e. obtains the axial displacement of the spindle 10; then calculating the axial dynamic stiffness k of the main shaft 10 according to the formula (1);
wherein, in the above formula (1):
x is the axial displacement of the spindle 10; s is the effective bearing area; n is0Is the rated rotational speed of the fixed displacement pump 70; n isxIs the rotational speed V1Or speed of rotation V2A variation amount (absolute value) with respect to the rated rotation speed; q. q.s0The rated oil amount pumped out for each rotation of the constant delivery pump 70; r0The resistance of the oil outlet liquid is adopted; h is0Is the initial gap size between the hydrostatic bearing 60 and the carrier plate 20.
It should be noted that the oil storage container 40 can be an oil storage tank, an oil storage barrel, an oil storage basin, etc.; the frequency converter 80 is a conventional component, and a method for implementing the power supply voltage control of the constant displacement pump 70 is known in the art, and will not be described herein.
In the process, the hydrostatic bearing 60 is matched with the constant delivery pump 70 to load the main shaft 10, and a gap exists between the hydrostatic bearing 60 and the bearing plate 20, so that safety accidents caused by collision and abrasion can be avoided; furthermore, the bearing plate 20 is not in contact with the hydrostatic bearing 60 in the operating state, and the oil film formed in the hydrostatic bearing 60 has a vibration absorption characteristic, so that vibration is reduced, and the bearing plate has excellent vibration absorption performance.
Further, the number of the displacement sensors 50 is two, the two displacement sensors 50 are sequentially arranged along the axial direction of the bearing plate 20, and then the average value of the values tested by the two displacement sensors 50 is taken as the axial displacement of the main shaft 10, so that the accuracy can be improved.
Specifically, the hydrostatic bearing 60 is further provided with an oil return groove 90 and an oil return passage 100; the notch of the oil return groove 90 faces the bearing plate 20; oil return groove 90 communicates oil return groove 90 with inner cavity 31; the oil return passage 100 is connected with an oil return pipe, and one end of the oil return pipe, which is far away from the oil return passage 100, extends into the oil storage container 40; thus, the oil ejected from the oil chamber 61 of the hydrostatic bearing enters the oil return groove 90 when passing through the position of the oil return groove 90, and then flows into the oil storage container 40 from the oil return passage 100 and the oil return pipe, so that the collection and recovery of part of the oil are realized, the oil splashing is avoided, and the cost is saved.
More specifically, the bearing seat 30 is provided with an oil return opening 110 communicating the outside with the inner cavity 31, so that the oil ejected from the oil cavity 61 of the hydrostatic bearing can flow into the oil storage container 40 from the oil return opening 110 when entering the inner cavity 31 and flowing to the cavity wall of the inner cavity 31, and further collection and recovery of the oil are realized.
The above embodiments are only preferred embodiments of the present invention, and the protection scope of the present invention is not limited thereby, and any insubstantial changes and substitutions made by those skilled in the art based on the present invention are within the protection scope of the present invention.
Claims (8)
1. A method for testing axial dynamic stiffness of a main shaft is characterized by comprising the following steps:
the preparation method comprises the following steps: a bearing plate is arranged on the main shaft; respectively arranging hydrostatic bearings at two opposite sides of the bearing plate along the axial direction of the main shaft in a clearance mode, enabling the initial clearances between the two hydrostatic bearings and the bearing plate to be the same, and enabling oil cavities of the two hydrostatic bearings to be oppositely arranged;
and a load applying step: driving the main shaft to rotate; two constant delivery pumps are adopted to respectively correspondingly input oil into the oil cavities of the two hydrostatic bearings, and the oil is sprayed to the bearing plate through the oil cavities of the hydrostatic bearings; at the same time, the rotating speed V of one of the constant delivery pumps is adjusted1Is adjusted to n0+nxAnd the rotational speed V of the other fixed displacement pump is adjusted2Is adjusted to n0-nx；
An axial displacement acquisition step: in the step of applying the load, a displacement sensor is adopted to test the axial displacement of the bearing plate, and the axial displacement x of the main shaft is determined according to the axial displacement of the bearing plate;
a calculation step:
calculating the effective bearing area S of the oil cavity of the hydrostatic bearing according to an area calculation formula;
calculating the oil outlet hydraulic resistance R of the oil cavity of the hydrostatic bearing0；
Calculating the axial dynamic stiffness k of the main shaft according to the formula (1);
wherein, in the above formula (1):
x is the axial displacement of the spindle; s is the effective bearing area of an oil cavity of the hydrostatic bearing; n is0The rated rotating speed of the fixed displacement pump; n isxIs the rotational speed V1Or speed of rotation V2A variation amount with respect to the rated rotation speed; q. q.s0The rated oil quantity pumped out by the fixed displacement pump every time the fixed displacement pump rotates one circle; r0The oil outlet hydraulic resistance of an oil cavity of the hydrostatic bearing is provided; h is0Is the initial gap size between the hydrostatic bearing and the carrier plate.
2. The axial dynamic stiffness testing method of a spindle according to claim 1, characterized in that: in the axial displacement obtaining step, the two displacement sensors are used for testing the axial displacement of the bearing plate, and the average value of the values tested by the two displacement sensors is taken as the axial displacement x of the main shaft.
3. The axial dynamic stiffness testing method of a spindle according to claim 1, characterized in that: in the step of applying the load, a frequency converter is adopted to control the frequency of a variable frequency motor supplied to the fixed displacement pump so as to adjust the rotating speed of the fixed displacement pump.
4. The axial dynamic stiffness testing method of a spindle according to claim 1, characterized in that: a flange is used as the carrier plate.
5. The utility model provides an axial dynamic stiffness testing arrangement of main shaft which characterized in that: the device comprises a bearing plate, a bearing seat, an oil storage container, a displacement sensor, two hydrostatic bearings, two constant delivery pumps and two frequency converters; the bearing seat is provided with an inner cavity; the bearing plate is movably arranged in the inner cavity; the two hydrostatic bearings are respectively arranged on two opposite sides of the bearing plate along the axial direction of the bearing plate and are respectively arranged on the bearing seats; the oil cavities of the two hydrostatic bearings are oppositely arranged, and a gap is formed between the hydrostatic bearings and the bearing plate; the two constant delivery pumps are arranged in one-to-one correspondence with the two hydrostatic bearings and are used for conveying the oil in the oil storage container to the oil cavities corresponding to the hydrostatic bearings; the two frequency converters are arranged in one-to-one correspondence with the two fixed displacement pumps; the output end of the frequency converter is electrically connected with the input end of the corresponding constant delivery pump, and the input end of the frequency converter is communicated with an external power supply; the displacement sensor is installed on the bearing seat and used for testing the axial displacement of the bearing plate.
6. The axial dynamic stiffness test device of a spindle according to claim 5, wherein: the number of the displacement sensors is two, and the two displacement sensors are sequentially arranged along the axial direction of the bearing plate.
7. The axial dynamic stiffness test device of a spindle according to claim 5, wherein: the hydrostatic bearing is also provided with an oil return groove and an oil return channel; the notch of the oil return groove faces the bearing plate; the oil return groove is communicated with the oil return groove and the inner cavity; the oil return passage is connected with an oil return pipe, and one end of the oil return pipe, which is far away from the oil return passage, extends into the oil storage container.
8. The axial dynamic stiffness test device of a spindle according to claim 5, wherein: the bearing seat is provided with an oil return port communicated with the outside and the inner cavity.
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| CN201811558812.2A CN109765016B (en) | 2018-12-19 | 2018-12-19 | Method and device for testing axial dynamic stiffness of main shaft |
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